JP2826106B2 - Hydraulic control device for automatic transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial applications)   The present invention relates to the operation of an automatic transmission provided in an automobile or the like.
Hydraulic pressure of automatic transmission controlled using hydraulic pressure
It relates to a control device. (Conventional technology)   Pumps and tarrs are used as automatic transmissions in automobiles.
A torque converter consisting of a bin and a stator,
Multi-stage gear type connected to the torque converter turbine
What is constructed in combination with a speed change mechanism is widely used
You. Such an automatic transmission usually includes a hydraulic circuit as a main component.
A hydraulic control device serving as a component is attached to the hydraulic control device.
The hydraulic pressure of the clutch, brake, etc. in the transmission mechanism
Fastening and release of actuated frictional engagement elements (frictional engagement elements)
Is performed, whereby the shift operation of the automatic transmission is performed.
You.   Automatic transmissions equipped with such a hydraulic control device
In addition, when the speed change operation is performed, for example,
-10851 and JP-B-62-18780.
In order to operate the friction fastening element,
As a result, an operating oil pressure to be supplied thereto is formed. In that case,
The shifting operation of the automatic transmission fastens the two friction fastening elements
From the released state to the released state or from the released state to the engaged state.
That is done by
Control to change the working oil pressure for one of the friction engagement elements and
Control to change the working oil pressure for the other friction engagement element
Must be performed individually. And like this 2
Control that changes the operating oil pressure for the two frictional engagement elements
When it is performed individually, do not involve shift shock etc.
One of the frictional engagements is required so that
Element is released from the engaged state or released from the engaged state
The other friction must be applied when the state is switched to the normal state.
Element is released from the released state at the appropriate time
It is desirable to switch from the engaged state to the released state
You. (Problems to be solved by the invention)   However, as described above, the two friction fastening elements
The control for changing the operating hydraulic pressure to be performed is a predetermined control feature.
Engine, torque,
Variations in the converter, friction fastening elements, etc.
Aging or temperature of hydraulic oil that generates hydraulic pressure
Due to fluctuations in environmental conditions such as temperature (oil temperature)
When the fastening element is released
The other friction with respect to the time of switching to the released state
Inappropriate timing when fastening elements are fastened or released
There is a possibility that it will become something.   In this way, one of the frictional engagement elements is engaged from the released state
State or switching from the engaged state to the released state.
Improper timing can lead to large shift shocks
And undesired rising of the engine speed
It is said that shifting in automatic transmission will not be performed smoothly
Problems arise.   In view of such a point, the present invention relates to a fluctuating dynamic in an automatic transmission.
Operating hydraulic pressure for each of the two friction engagement elements
The control to change is performed individually.
State switch from the disengaged state to the engaged state
The other friction engagement element is in the engaged state with respect to the
The timing of switching the state from
An automatic transmission designed to prevent accidents
It is an object of the present invention to provide a hydraulic control device. (Means for solving the problem)   To achieve the above object, an automatic transmission according to the present invention
The hydraulic control device has a structure as shown in FIG.
And the first and second gear shift operations in the automatic transmission.
First adjusting the working oil pressure supplied to each of the friction engagement elements;
And second solenoid means, and first and second frictional engagements
The first frictional engagement element is
State change from release state to engagement state and second frictional engagement
State switching from the engaged state to the released state
First and second eyes to be performed with overlapping times
Setting the target oil pressure and the operation supplied to the first friction engagement element
A first solenoid means for adjusting the hydraulic pressure, and a second friction means.
A second solenoid for adjusting the working oil pressure supplied to the friction engagement element
Set the first and second target hydraulic pressures of the
Therefore, drive control is performed so that the first target
The operating oil pressure according to the oil pressure is supplied and the second friction
The working oil pressure according to the second target oil pressure is supplied to the friction engagement element.
And a hydraulic control means provided in the automatic transmission.
To detect the rotational state of the turbine of the torque converter
In addition to the provision of
Each of the first and second solenoid means by the control means
Drive control is opened in accordance with the first and second target hydraulic pressures.
Detected by the turbine condition detecting means
Of the turbine speed based on the
Whether a blow-up or pull-in phenomenon has occurred
Judgment and the result of the judgment is sent to the hydraulic control
When the number-up phenomenon occurs, the first
Third and second target hydraulic pressures greater than the target hydraulic pressure
By setting a smaller fourth target oil pressure, the first solenoid
Instead of using the first target hydraulic pressure instead of the first target hydraulic pressure.
Drive control and the second solenoid means
Drive control according to the fourth target oil pressure instead of the second target oil pressure
And the result of the judgment is that the turbine
When we show that the number entrainment phenomenon has occurred, the first
The fifth target hydraulic pressure and the second target hydraulic pressure that are smaller than the target hydraulic pressure
The sixth target hydraulic pressure is set to
In accordance with the fifth target hydraulic pressure instead of the first target hydraulic pressure.
Drive control and the second solenoid means to the second
Drive control is performed according to the sixth target hydraulic pressure instead of the target hydraulic pressure of
And a target oil pressure change control means for
Be composed. (Operation)   The automatic transmission according to the present invention having the configuration as described above
In the hydraulic control device, the target hydraulic pressure change control means
Switching of the state of the first frictional engagement element from the released state to the engaged state
Is started according to the first target oil pressure, and the second
Switching of the frictional engagement element from the engaged state to the released state
Started according to a second target hydraulic pressure, the turbine
Based on the rotation state of the turbine detected by the state detection means
Then, a determination is made as to the rotation speed of the turbine. Soshi
Thus, the result of the determination by the target hydraulic pressure change control means is as follows:
The fact that the turbine speed rose
In the case that the
The step moves the first frictional engagement element from the released state to the engaged state.
The state switching is performed using the first target hydraulic pressure instead of the first target hydraulic pressure.
If we continue according to the third target oil pressure that is larger than the oil pressure,
In addition, the second frictional engagement element is changed from the fastened state to the released state.
The state switching is performed using the second target hydraulic pressure instead of the second target hydraulic pressure.
State to continue according to a fourth target oil pressure lower than oil pressure
It is said. On the other hand, the result of the judgment by the target oil pressure change control means
As a result, the fact that the turbine rotation speed
In this case, the target hydraulic pressure change control means
The control means changes the first frictional engagement element from a released state to a fastened state.
Is changed to the first target hydraulic pressure instead of the first target hydraulic pressure.
Continue according to a fifth target oil pressure lower than the target oil pressure
And the second frictional engagement element is released from the engaged state.
Is changed to the second target oil pressure,
Continue according to the sixth target oil pressure that is larger than the target oil pressure of
State.   By doing so, the first frictional engagement element
From the release state to the engagement state
From the engaged state to the released state of the friction engagement element
The period up to the switching time is considered to be appropriate and
Shift shock or undesired increase in engine speed
The occurrence of the peeling phenomenon and the like is suppressed. (Example)   Hereinafter, embodiments of the present invention will be described with reference to the drawings.   FIG. 2 is a hydraulic control device for an automatic transmission according to the present invention.
FIG. 3 shows a main part of an example, and FIG. 3 shows an automatic transmission according to the present invention.
The main part of an automatic transmission to which an example of a hydraulic control device is applied
Shown schematically.   In FIG. 3, the crankshaft 10 of the engine
While the pump 14 of the torque converter 12 is connected,
Rotary shaft of oil pump 50 via pump drive shaft 16
Are connected. Turbine 18 for torque converter 12
Is a multi-stage gear type transmission via a hollow turbine shaft 17
The lock-up clutch 22
Connected to the crankshaft 10 via the
The stator 13 of the motor 12 and the case 21 of the torque converter 12.
A one-way clutch 19 is interposed between
The data 13 rotates in the same direction as the pump 14 and the turbine 18.
It has been made.   The multi-stage gear type transmission mechanism 20 has four forward stages and one reverse stage.
And a planetary gear unit 24. Planeta
Regear unit 24, small diameter sun gear 25, large diameter sun gear 2
6, long pinion gear 27, short pinion gear 28, and
And a ring gear 29. Small diameter sun gear
Between the turbine shaft 17 and the turbine shaft 17
Word clutch 31 and coast clutch 33 are installed side by side,
One between the small diameter sun gear 25 and the forward clutch 31
A way clutch 32 is interposed. With large diameter sun gear 26
There is a reverse for reverse running between the turbine shaft 17
A clutch 35 is provided and a 2-4 brake 36
It is arranged. 2-4 brake 36 is large diameter sun gear 26
Brake drum 36a and this brake drum 3
6a with a brake band 36b for tightening
Have been. In addition, the long pinion gear 27 and the turbine
A 3-4 clutch 38 is provided between the shaft 17 and the
The pinion gear 27 includes a carrier 39 and a one-way clutch 41.
Is connected to the transmission case 42 through the
Machine case 42 is disengaged by low reverse brake 44
It has been made like that. The ring gear 29 is
Connected to the output gear 47 via the output shaft 45
ing.   In the multi-stage gear type transmission mechanism 20 having such a configuration,
Is the forward clutch 31, coast clutch 33, river
Scratch 35 and 3-4 clutch 38,2-4 brake 36,
And selectively operate the low reverse brake 44 as appropriate.
By making the P range (parking range), R
Range, N range, F range (forward range)
D range, 2 range and 1 range, and F range
And the first to fourth speeds. So
These clutches and gears to obtain each range and gear
When the rake operation relationship and each range and gear are obtained
Operating states of the one-way clutches 32 and 41 during
It is shown in Table 1. In addition, of each clutch and brake, 2-
The four brakes 36 are provided on two sides, a supply side and a discharge side, as described later.
When the operating oil pressure is supplied to the oil chamber on the supply side
Only when the operating oil pressure is removed from the oil chamber on the discharge side
Takes the engaged state, and releases it in other working hydraulic pressure supply states.
Each clutch and other than the 2-4 brake 36
And brakes each have only one oil chamber,
When the operating oil pressure is supplied to the
Release when hydraulic pressure is removed from the
It is.   Referring to FIG.
The operating oil pressure obtained from the oil pump 50
The pressure is regulated by the lube 52 and passes through the oil passage 100 and its branch passage.
Manual valve 54, 1-2 shift valve 55, course
Toy exhaust valve 56, 2-3 shift valve 57, lock
Up clutch control valve 58, converter lily
Guided to the safety valve 59 and the servo control valve 60.
You. The hydraulic pressure guided to each valve is the line pressure.
You.   The manual valve 54 includes a shift lever (not shown) and the like.
By operating the shift range switching means of the
6, R range, N range, D range, 2 range and 1 range
One of the three range positions can be selectively taken.
The manual valve 54 is connected to the output ports a, c, e and f.
It has an input port g connected to the oil passage 100,
Dual valve 54 for 1 range, 2 range and D range
When taking, the input port g is connected to the output port a, the oil passage 101
And 111, forward control valve 65 and oil passage 112
And connected to the forward clutch 31 via
Output port a, part of oil passage 101 and oil passage 111, oil passage 113,
Stig exhaust valve 56, oil passage 115, coast control
The coast clutch 3 is connected via the
3 and the output port a, oil
Via the shift valve 55 and the oil passage 118,
4 The state where it can be connected to the supply side oil chamber 36B of the brake 36
Output port a, oil passage 101, oil passage 119,
2-4 strokes via control valve 60 and oil passage 120
That can be connected to the discharge-side oil chamber 36A of the
You.   And the manual valve 54 has 2 ranges and D range
When taking the position, the input port g is connected to the output port c, oil
Road 103, 2-3 shift valve 57, oil line 121, clutch control
3-4 clutch 38 via the valve 67 and the oil passage 122.
And the manual valve 54 is
Input port g is the output port
e, oil passage 105, low reducing valve 69, oil passage 125,
1-2 via the shift valve 55, the switching valve 70, and the oil passage 126,
Connected to low reverse brake 44 and output port
Coast e exhaust valve via oil e and oilway 139
Connected to the bus 56.   When the manual valve 54 is in the R range position
Has an input port g, an output port f, a part of the oil passage 106,
Low reverse vibration is performed via the switching valve 70 and the oil passage 126.
Output port f, oil passage 106,
Reverse control valve 66
Connected to 35. Then, the manual valve 54 is
Input port g when taking the
Is not connected to any of the output ports a, c, e and f.
Therefore, in such a case, the multi-stage gear type speed change mechanism 20
, Forward clutch 31, coast clutch 33, river
Source clutch 35, 2-4 brake 36, 3-4 clutch 38, b
-Reverse brake 44 and lock-up clutch 22
And the turbine 18 is idled.   On the other hand, the operating oil pressure obtained from the oil pump 50 is
110 to solenoid reducing valve 53
And the pressure is reduced to a predetermined pressure.
As described later, the first, second, third, and fourth duty
The oil pressure is regulated by the solenoid valves 61, 62, 63 and 64,
Servo control valve through 131, 132, 133 and 134
60, reverse control valve 66, clutch control
Valve 67, lock-up clutch control valve
Valve 58 and regulator valve 52 with their pilot
Supplied as pressure.   The servo control valve 60 has a 2-4 brake 36
The operating oil pressure guided from the discharge side oil chamber 36A through the oil passage 120 is
It is supposed to regulate the pressure, and the servo control valve
The working oil pressure regulated by
Supplied as pilot pressure for strike control valve 68
As well as the forward control valve 65.
Be paid.   The pilot pressure for the 2-3 shift valve 57 described above
Supply is performed through an oil passage 111a branched from the oil passage 111.
However, the supply and stop of the pilot pressure is 2-3
Controlled by a solenoid valve 72, a 2-3 solenoid valve
When the lube 72 is turned on, the operating pressure oil from the oil passage 111a is
Pyro discharged to reservoir and sent to 2-3 shift valve 57
The supply of the cut pressure is stopped, and the 2-3 solenoid valve 72 is
When taking the off state, the pilot valve
Pressure is supplied. Supplied to 2-3 shift valve 57
The pilot pressure is changed through the oil passage 138 to the 1-2 shift valve 55.
And the oil passage 138 is connected to the 1-2 shift valve 55.
Branch from pilot pressure and oil passage 100 supplied through
Both pilot pressure supplied through oil passage 100a
Be paid. Provided to the 1-2 shift valve 55 through the oil passage 100a.
Supply and stop of the supplied pilot pressure is performed by 1-2 solenoid
Controlled by the id valve 71, 1-2 solenoid valve
When the valve 71 is turned on, the operating pressure oil from the oil passage 100a
Pyro discharged to reservoir and shifted to 1-2 shift valve 55
Supply of cut pressure is stopped, and the 1-2 solenoid valve 71 is
When taking the off state, the pilot valve
Pressure is supplied. In addition, pilot
When pressure is supplied to the 1-2 shift valve 55, 1-
Regardless of ON / OFF state of 2 solenoid valve 71
The spool of the 1-2 shift valve 55 is shown in FIG.
Pushed to the right, the oil passage 101 and the oil passage 118 are brought into communication.
You. Then, the 1-2 solenoid valve 71 and the 2-3 solenoid
ON / OFF state of the solenoid valve 72, shift range and shift
The relationship with the steps is as shown in Table 2.  In addition, a parameter controlled by the 1-2 solenoid valve 71
Illot pressure is also supplied to coast exhaust valve 56.
The coast exhaust valve 56 has an additional manifold.
When the dual valve 54 is in the 1 range position, the output port
e and the pilot pressure is supplied via the oil passage 139. Ko
The exhaust valve 56 controls their pilot pressure.
Is supplied to coast clutch 33 by supply and removal of
The operating oil pressure is intermittent.   In the present example having such a configuration, as shown in FIG.
As described above, the above-described first to fourth duty solenoid valves
Lube 61-64, 1-2 solenoid valve 71 and 2-3 solenoid
The control unit is used to control the operation of the
A knit 200 is provided. Control unit 200
The shift position of the shift lever 92 and therefore the manual
Shift position sensor that detects the range position of valve 54
The detection signal Ss obtained from the
Detection signal obtained from the detected turbine speed sensor 94
St, detection signal obtained from the vehicle speed sensor 96 that detects the vehicle speed
Detects Sv and engine load such as throttle valve opening
And a detection signal Sl obtained from the load sensor 97.
Together with other checks required to control the automatic transmission.
An outgoing signal Sx is also provided.   The control unit 200 receives the various detection signals described above.
Form drive pulse signals Ca, Cb, Cc and Cd based on
And the first to fourth duty solenoid valves
Supply to 61 to 64 respectively, and the detection signal Sv
Based on the vehicle speed and the engine load represented by the detection signal Sl
To form open / close drive signals Ce and Cf, and
The solenoid valve 71 and the 2-3 solenoid valve 72
Supply each.   As a result, the servo control valve 60, reverse
Control valve 66, clutch control valve 67,
Lock-up clutch control 58, regulator cover
Lube 52, 1-2 shift valve 55 and 2-3 shift valve 57
The pilot pressure supplied to the automatic transmission is adjusted
Forward clutch 31, coast clutch 33, river
Source clutch 35,3-4 clutch 38,2-4 brake 36 and
As shown in Table 1 above, the low reverse brake 44
In addition, it is selectively engaged or released,
The shift range and the shift speed are obtained.   In that case, the control unit 200
Built-in when -92 is in D range, 2 range, 1 range position
Shift pattern mapped and stored in the memory
The vehicle speed and the detection signal Sl are represented by the
System that switches gears based on the engine load
I will do it. In performing such shift stage switching control,
Control unit 200 is, for example, an automatic transmission.
The shift range is in the D range or 2 range
Switch from 2nd gear to 3rd gear (hereinafter 2-3 shift)
Is performed as follows.   When the control unit 200 is in the second speed,
1-2 solenoid valve 71 and 2-3 solenoid
The open / close drive signals Ce and Cf are supplied to the
Are turned on, and the first and second duties are turned on.
Drive pulses supplied to the solenoid valves 61 and 62
For example, the pulse occupancy of the signals Ca and Cb is set to zero, and
Maximize these valve opening periods and use servo control valves
Pie supplied to 60 and clutch control valve 67
Minimize lot pressure. Thereby, 3-4 clutch
38, the supply of hydraulic pressure to the
The operating oil pressure is supplied to the supply-side oil chamber 36B of the key 36.
The operating oil pressure is supplied to the discharge side oil chamber 36A of the 4 brake 36.
Therefore, in such a case, the 3-4 clutch 38 is released.
Released and 2-4 brake 36 engaged
It is said.   Then, the control unit 200 outputs the detection signal Sv
The engine speed indicated by the vehicle speed or detection signal Sl
The load has a value that should be shifted up by 2-3.
The friction engagement element for high speed gear (friction engagement element)
Switching a certain 3-4 clutch 38 from the released state to the engaged state
And a low-speed gear friction fastening element
2-4 brake 36 from the engaged state to the released state
Open for 2-3 solenoid valve 72 to be switched
Stop the supply of the closing drive signal Cf and turn it off,
The second and first duty solenoid valves 62 and
The pulse occupancy of the drive pulse signals Cb and Ca supplied to 61
To increase the hydraulic pressure supplied to the 3-4 clutch 38.
As it increases, the oil chamber 36A on the discharge side of the 2-4 brake 36
Control to increase the operating oil pressure supplied to the motor.   When such control is performed, for example, the hydraulic pressure Px
In FIG. 5, the horizontal axis represents the distance t between the axes.
In the 3-4 clutch 38 as shown by the dashed line.
Reference target oil pressure TPc and 2-4
The reference target oil pressure TPb for the discharge side oil chamber 36A of the rake 36 is
Is set. Reference target oil pressure TPc is shifted up by 2-3
Start time t₁Is set to zero at time t₁From given
Time t when period Ta elapses_TwoAt the value P₁Set to
Point t_TwoFrom the time t when the period Tb elapses_FiveAt the value P₁Younger
Insane value P_TwoSet at time t_FivePeriod Tc has passed since
Time t₆Is the maximum value PL. In addition, the standard target oil
Pressure TPb at time t₁T when a predetermined period Tα elapses from_Three
Is set to zero until time t_ThreeA predetermined period Td has elapsed since
Time t_FourAt the value P_TwoGreater value P_ThreeSet to
Point t_FourT when a predetermined period Te elapses from₇At the value P_Three
A slightly larger value P_FourSet at time t₇From the specified period
Time t when Tf elapses₈Is the maximum value PL.   The control unit 200 is set as described above
With a pulse occupancy corresponding to the reference target hydraulic pressure TPc
Forming a dynamic pulse signal Cd,
Supply to the solenoid valve 62 and the reference target oil pressure TP
A drive pulse signal Ca corresponding to b is formed and
Is supplied to the duty solenoid valve 61. It
Oil on the discharge side of the 3-4 clutch 38 and the 2-4 brake 36
The working hydraulic pressure supplied to the chamber 36A depends on the engine and automatic transmission.
No variation or aging has occurred in the oil
Under ideal conditions where environmental conditions are assumed to be stable,
Time t₁From then on, it will generally follow the reference target oil pressures TPc and TPb.
And the 3-4 clutch 38 is
It is assumed that the change in hydraulic pressure corresponding to the period Tb is relatively small.
Half-fastened state during the period when the operating hydraulic pressure is supplied
To the engaged state, and the 2-4 brake
36 has a relatively small change in hydraulic pressure corresponding to the above-described period Te.
During the period when the operating hydraulic pressure
Thus, the state is shifted from the semi-released state to the released state.   Thus, the 3-4 clutch 38 is closed from the released state.
And the 2-4 brake 36
From the engaged state to the released state, and 2-3
Under the upshift, the 3-4 clutch 38
2-4 brake 36 is released for the time of engagement
The time to enter the state becomes appropriate, and the turbine speed NT
Is changed, for example, as shown by the solid line in FIG. 6A.
It will become. In addition, FIG.
Changes in vehicle speed V before and after the shift up period
Is shown.   6A and 6B, for example, when the vehicle speed V is 2-3
Value V at which lift-up should take place₁Reached the above time t₁To
Corresponding time t_aAfter that, the turbine rotation speed NT
Switch 38 is released while the brake 38 is engaged.
And the value N_TwoTransmission ratio in 2nd gear state and 3rd gear state
3-4 clutch
38 is engaged and the 2-4 brake 36 is released.
Time t_bThe value N which is the minimum at₁And then
It will start to rise. Such time t_aFrom time t_bTo
The vehicle speed V is equal to the value V₁Rising from the value V_TwoTona
And then rise, but at time t_aFrom time t_b
Changes in the vehicle speed V during this period are extremely small. This
And the turbine speed NT and the vehicle speed V change
At time t_bOf the turbine speed NT at N₁Is the third speed
If the gear ratio in the state is K, then N₁= V × K × C (however
And C is a constant).   However, as mentioned above, usually, the engine and automatic transmission
The machine may fluctuate or aging, and may be subject to environmental conditions such as oil temperature.
Since the conditions fluctuate, the base shown in FIG.
Based on the semi-target hydraulic pressures TPc and TPb, the 3-4 clutch 38
And operation supplied to the discharge speed oil chamber 36A of the 2-4 brake 36
When the oil pressure is changed, the 3-4 clutch 38 is engaged.
2-4 brake 36 is released when
The timing may be incorrect. In that case, 3-
2-4 with respect to the time when the four clutches 38 are engaged.
If the brake 36 is released too soon,
The bin rotation speed NT is indicated by a chain line in FIG. 6A.
As described above, the time point t when the appropriate shift is performed_bThan
Early time t_b', The value N₁Greater minimum N₁′
And the turbine speed NT rises.
I will. On the other hand, the 3-4 clutch 38 is engaged.
When the 2-4 brake 36 is released against the time
If the period is too late, the turbine speed NT
As shown by the broken line,
Time t_bLater time t_bThe value N at ″₁Less than
Minimum N₁”To reduce the turbine speed NT.
A burning phenomenon occurs.   In this way, the turbine speed NT
When the engine stagnation occurs, the engine speed
Automatic transmission
In this case, a smooth shift is not performed. Therefore,
In this example, the control unit 200
During the first 2-3 shift ups in time,
First, the reference target oil pressures TPc and TPb as shown in FIG.
Therefore, the discharge of the 3-4 clutch 38 and the 2-4 brake 36
It is adjusted to the working oil pressure supplied to the side oil chamber 36A. And
During the 2-3 shift up, the turbine speed NT
Calculate the rate of change, and at the point where the rate of change first becomes zero,
That is, the minimum value of the turbine speed NT is detected, and the detected pole
The small value depends on the vehicle speed V and the gear ratio in the third speed state.
The value N shown in FIG. 6₁Na near
It is determined below whether or not it is in the range of the value Nb or more, and the value N₁In the vicinity
If it is determined that there is an appropriate
Therefore, even in the following 2-3 shift-up,
Set the reference target oil pressures TPc and TPb as shown in FIG.
You.   On the other hand, the detected minimum value is the value N₁Not in the vicinity
If it is determined that the value is larger than
Indicates that the turbine speed NT
In the following 2-3 shift up,
The first changed target hydraulic pressure TP as shown in FIG.
c ′ and TPb ′ are set, and the detected minimum value is a value N₁
Judgment that it is not nearby and takes a smaller value
Cause the pull-in phenomenon of the turbine speed NT.
For the upcoming 2-3 shift up
Is the second change, as shown in FIG.
Set the target oil pressures TPc ″ and TPb ″.   In FIG. 7, the first changed target hydraulic pressure TPc '
₁From the predetermined period T longer than the period Ta shown in FIG.
time t when a ′ elapses_Two′, The value P₁Greater value P
₁′ At time t_TwoA predetermined period Tb ′ shorter than the period Tb
Elapses t_Five′, The value P_TwoGreater value P_Two′
At time t_Five′ To a predetermined period T slightly longer than the period Tc
time t when c ′ elapses₆′, The maximum value PL is
And the first changed target hydraulic pressure TPb ′ is₁
From the predetermined period T longer than the period Tα shown in FIG.
time point when β elapses_Three′ To zero, and time t_ThreeFrom '
Time t when a period Td ′ shorter than the period Td elapses_Four′
Value P_ThreeLesser value P_Three′ At time t_Four′ From period Te
Time point t at which a short predetermined period Te ′ elapses₇', The value
P_FourLesser value P_Four′ At time t₇若 younger than period Tf
The point in time t when the predetermined period Tf ′ elapses₈′
It is assumed to take the maximum value PL.   According to the first changed target oil pressures TPc ′ and TPb ′ as described above,
The discharge side of the 3-4 clutch 38 and the 2-4 brake 36
By adjusting the operating oil pressure supplied to the oil chamber 36A,
In accordance with the reference target oil pressures TPc and TPb shown in FIG.
When the 3-4 clutch 38 is engaged
And the 2-4 brake 36 is released
3-4 clutch 38
When the state switches from the released state to the engaged state and 2
-4 Brake 36 switches state from engaged state to released state
The relative relationship with the timing of the
As a result, the 3-4 clutch 38 is engaged.
The time when the 2-4 brake 36 is released compared to the time
Is appropriate and the turbine speed NT
The elephant will be suppressed.   On the other hand, the second changed target oil pressure TPc ″ shown in FIG.
At time t₁From the predetermined time shorter than the period Ta shown in FIG.
The time t when the period Ta ″ elapses_TwoThe value P₁Smaller
Value P₁″, At time t_TwoFrom "" a predetermined period that is approximately the same as period Tb
The time t when the interval Tb ″ elapses_FiveThe value P_TwoLess than
Value P_Two″, At time t_Five″ To period T slightly shorter than period Tc
time t when c ″ elapses₆″ Takes the maximum value PL,
Further, the second changed target hydraulic pressure TPb ′₁To period T
Time point t when a predetermined period Tγ shorter than α elapses_ThreeUp to zero
At time t_ThreeA predetermined period Td longer than the period Td from "
Time t_FourThe value P_ThreeGreater value P_Three″
At time t_Four"The predetermined period Te longer than the period Te" elapses
Time t₇The value P_FourGreater value P_Four″
At time t₇A predetermined period Tf shorter than the period Tf has elapsed since ″
Time t₈”Means the maximum value PL
You.   As described above, the second change target hydraulic pressures TPc ″ and TPb ′
Therefore, the discharge of the 3-4 clutch 38 and the 2-4 brake 36
The working oil pressure supplied to the side oil chamber 36A is adjusted.
In accordance with the reference target oil pressures TPc and TPb shown in FIG.
When the 3-4 clutch 38 is engaged
And the 2-4 brake 36 is released
3-4 clutch 38
When the state switches from the released state to the engaged state and 2
-4 Brake 36 switches state from engaged state to released state
The relative relationship of when to do
As a result, when the 3-4 clutch 38 is engaged
On the other hand, when the 2-4 brake 36 is released
And the phenomenon of pulling in the turbine speed NT
Will be suppressed.   As described above, the turbine rotational speed NT during shifting
The control according to "is performed, ...
The “shift shock” is changed to “3-4
After the clutch 38 has been engaged,
And the 2-4 brake 36 is released,
Shifting shock or undesired blowing of engine speed
The occurrence of the rising phenomenon is effectively prevented.   Control unit 200 that performs control as described above
Is configured using, for example, a microcomputer.
However, in such a case, the microcomputer
Running, mainly first and second duty solenoids
An example of a program for controlling the operation of the valves 61 and 62
With reference to the flowcharts shown in FIGS. 9 and 10.
I will explain.   The program shown in FIG. 9 is a basic shift control routine.
This routine indicates, for example, that the engine is
Start when the process starts, and in process 201
Capture detection signals St, Sv, Ss, Sl, etc.
In step 202, the shift pattern stored in the internal memory is
The vehicle speed V represented by the detection signal Sv and the detection signal Sl.
The engine load and the shift level represented by the detection signal Ss.
Perform 2-3 upshifts based on the position of bar 92.
Judge whether or not the condition is satisfied, and shift up by 2-3
If it is determined that the conditions for performing
Sets the 2-3 shift flag R to zero in the process 203.
Reset, and a 2-3 shift
Return to the original state after performing gear change control other than
The condition to perform 2-3 up-up is satisfied in 2
If it is determined that the
-4 Set the shift flag R to 1 and proceed to process 206.
Control to turn off 2-3 solenoid valve 712
After that, go to decision 207.   In the decision 207, the setting completion flag F is set to 1
(Set state) to determine whether or not the setting complete flag
If it is determined that F is not 1, the process 208 is executed.
And the reference target oil pressures TPb and TPc as shown in FIG.
According to the first and second duty solenoid valves
After performing the drive control of 61 and 62, it returns to the original state. In addition,
Judged that the setting completion flag F is 1 in John 207
If so, at process 209, as shown in FIG.
Target hydraulic pressure set in the target hydraulic pressure setting routine
According to the first and second duty solenoid valves
After performing the drive control of 61 and 62, it returns to the original state.   FIG. 10 shows a target hydraulic pressure setting routine.
After the start, the detection signal is detected in the process 210.
Nos. St and Sv, and in Decision 213
It is determined whether the 2-3 shift flag R is 1 or not.
If it is determined that the 3 shift flag R is not 1,
Return if the 2-3 shift flag R is determined to be 1
In this case, the setting completion flag F
It is determined whether it is 1 or not, and the setting completion flag F is 1
If the setting completion flag F is set to 1
If not, at process 215,
The detection signal St captured in the previous flow appears.
Value N of turbine rotation speed NT_n-1From, newly imported
Subtract the value Nn of the turbine speed Nt represented by the detection signal St
The difference ΔN is calculated, and then the difference
It is determined whether ΔN is equal to or smaller than a value α slightly larger than zero, and the difference Δ
If it is determined that N is not less than the value α, the process returns to
If ΔN is determined to be less than or equal to the value α,
Proceed to option 218.   In decision 218, the value N of the turbine speed NT
n is determined by the vehicle speed V and the gear ratio K in the third speed state.
Judge whether it is more than the value Nx which is slightly larger than
If Nn is determined to be greater than or equal to the value Nx, the process 21
In 9, the first change target as shown in FIG.
Set the hydraulic pressures TPc 'and TPb' and set them in process 220.
The fixed completion flag F is set to 1 and the process returns. Also,
In the case 218, the value Nn of the turbine speed NT is equal to the value Nx.
If it is determined to be less than
The value Nn determines the vehicle speed V according to the speed ratio K in the third speed state.
Is smaller than the value Ny slightly smaller than the value determined by
Is determined, and when it is determined that the value Nn is equal to or less than the value Ny,
Is the process 224, as shown in FIG.
The second change target oil pressure TPc ″ and TPb ″ is set, and the process is performed.
At 220, set the setting completion flag F to 1 and return to the original
In the decision 222, the value Nn is not less than the value Nb.
If so, the process 223 returns to FIG.
Set the reference target hydraulic pressures TPc and TPb as shown in
Set the setting completion flag F to 1 in process 220
Return to the original.   Note that, in the example described above, the time during shifting is changed.
-Based on the minimum value of bin rotation speed NT, two friction fastening
The control characteristics in the control of the supply of hydraulic pressure to the element
It is made to change in stages, but according to the present invention
Hydraulic control device of automatic transmission is limited to it, two friction
Control Characteristics of Hydraulic Pressure Supply Control for Fastening Elements
Is changed in three or more steps or continuously.
May be used to change the control characteristics.
As in the above example,
Instead of doing so based on the local minimum of the number NT, for example,
It is performed based on the rate of change of the bin rotation speed NT, etc.
Is also good.   In the above example, the turbine speed is increased.
When the sticking phenomenon or the pull-in phenomenon occurs at the end of the fluctuation operation
However, the hydraulic control of the automatic transmission according to the present invention is described.
The control device controls the speed
The same applies to cases that occur at the start of operation.
If the rate of change first becomes zero,
-The value of the bin rotation speed and the speed ratio in the vehicle speed and the second speed state
According to the difference from the value of the turbine speed determined accordingly,
When the 4 brake 36 is released and the 3-4 clutch
38 to adjust the relative relationship to when it is in the engaged state
What should I do?   Further, in the above-described example, the gear position of the automatic transmission
Explains the case where the gear can be switched from 2nd gear to 3rd gear.
However, the hydraulic control device of the automatic transmission according to the present invention
Not limited to this, two friction fastening
Other changes made by switching the element
The same applies to high-speed operation. (The invention's effect)   As is apparent from the above description, the automatic transmission according to the present invention
According to the hydraulic control device of the engine, the engine, torque converter
Data, frictional engagement elements, etc.
Even if environmental conditions such as oil temperature change, the first frictional engagement
Timing of state switching from disengaged state to engaged state in element
From the engaged state to the released state of the second frictional engagement element
The period until the time of status change shall be appropriate
So that a large shift shock or
Undesirable engine speed rises
It can be effectively prevented from spreading.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a basic configuration diagram showing a hydraulic control device for an automatic transmission according to the present invention according to the claims, and FIG. 2 is a hydraulic control for the automatic transmission according to the present invention. FIG. 3 is a diagram showing a main part of a hydraulic circuit in an example of the apparatus, FIG. 3 is a diagram schematically showing a main part of an automatic transmission to which the example shown in FIG. 2 is applied, and FIG. 4 is a diagram shown in FIG. Schematic diagram of the electronic control system of the example shown in FIG.
FIGS. 6, 6, 7 and 8 are time charts for explaining the operation of the example shown in FIG. 2, and FIGS. 9 and 10 are the control units of the example shown in FIG. 4 is a flowchart illustrating an example of a program executed by a microcomputer when the microcomputer is used. In the figure, 31 is a forward clutch, 36 is 2-4 brake,
38 is a 3-4 clutch, 54 is a manual valve, 55 is 1-
2 shift valve, 56 is a coast exhaust valve, 6
1, 62, 63 and 64 are first, second, third and fourth duty solenoid valves, 92 is a shift lever, 93 is a shift position sensor, 94 is a turbine speed sensor, 96 is a vehicle speed sensor, and 97 is a load. The sensor 200 is a control unit.

Continuation of front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F16H 61/04-61/08

Claims (1)

(57) [Claims] A first adjusting operation hydraulic pressure respectively supplied to first and second friction engagement elements that perform a shift operation in the automatic transmission;
And second solenoid means, and the first frictional engagement element is switched from a released state to an engaged state and the second frictional engagement element is caused to perform the fluctuating operation by the first and second frictional engagement elements. The first and second target hydraulic pressures for causing the friction engagement elements to switch from the engaged state to the released state at mutually overlapping timings are set and supplied to the first friction engagement element. The first solenoid means for adjusting the working oil pressure and the second solenoid means for adjusting the working oil pressure supplied to the second frictional engagement element are provided in accordance with the first and second target oil pressures, respectively. A drive hydraulic pressure is supplied to the first frictional engagement element according to the first target hydraulic pressure by drive control,
Hydraulic control means for supplying a working oil pressure according to the second target oil pressure to the second friction engagement element, and a turbine for detecting a rotation state of a turbine of a torque converter provided in the automatic transmission The state detection means, and the drive control of each of the first and second solenoid means by the hydraulic pressure control means are started by the turbine state detection means in accordance with the first and second target oil pressures. Based on the rotation state of the turbine, it is determined whether a rising phenomenon or a retraction phenomenon of the rotation speed of the turbine has occurred. When the third target hydraulic pressure is higher than the first target hydraulic pressure and the fourth target hydraulic pressure is lower than the second target hydraulic pressure. And the drive control of the first solenoid means is performed according to the third target oil pressure instead of the first target oil pressure, and the second solenoid means is controlled by the second target oil pressure instead of the second target oil pressure. When the drive control is performed in accordance with the fourth target hydraulic pressure, and the result of the determination indicates that the pull-in phenomenon of the turbine rotational speed has occurred, the fifth target hydraulic pressure which is smaller than the first target hydraulic pressure is set.
And a sixth target oil pressure that is larger than the second target oil pressure, and the first solenoid means is set to the first oil pressure.
Drive control is performed in accordance with the fifth target hydraulic pressure instead of the target hydraulic pressure, and the second solenoid means is controlled by the second target hydraulic pressure.
And a target hydraulic pressure change control means for controlling the drive in accordance with the sixth target hydraulic pressure instead of the target hydraulic pressure.